WO2007009874A1 - Installation a turbine a gaz et a vapeur, ainsi que procede pour la faire fonctionner - Google Patents

Installation a turbine a gaz et a vapeur, ainsi que procede pour la faire fonctionner Download PDF

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Publication number
WO2007009874A1
WO2007009874A1 PCT/EP2006/063874 EP2006063874W WO2007009874A1 WO 2007009874 A1 WO2007009874 A1 WO 2007009874A1 EP 2006063874 W EP2006063874 W EP 2006063874W WO 2007009874 A1 WO2007009874 A1 WO 2007009874A1
Authority
WO
WIPO (PCT)
Prior art keywords
pressure stage
steam turbine
gas
steam
low
Prior art date
Application number
PCT/EP2006/063874
Other languages
German (de)
English (en)
Inventor
Herbert Schütz
Holger-Max Emberger
Martin Weinberger
Original Assignee
Siemens Aktiengesellschaft
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Siemens Aktiengesellschaft filed Critical Siemens Aktiengesellschaft
Priority to EP06777567.6A priority Critical patent/EP1904731B1/fr
Publication of WO2007009874A1 publication Critical patent/WO2007009874A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
    • F02C6/00—Plural gas-turbine plants; Combinations of gas-turbine plants with other apparatus; Adaptations of gas-turbine plants for special use
    • F02C6/18—Plural gas-turbine plants; Combinations of gas-turbine plants with other apparatus; Adaptations of gas-turbine plants for special use using the waste heat of gas-turbine plants outside the plants themselves, e.g. gas-turbine power heat plants
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
    • F02C7/00—Features, components parts, details or accessories, not provided for in, or of interest apart form groups F02C1/00 - F02C6/00; Air intakes for jet-propulsion plants
    • F02C7/36—Power transmission arrangements between the different shafts of the gas turbine plant, or between the gas-turbine plant and the power user
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2220/00—Application
    • F05D2220/70—Application in combination with
    • F05D2220/72—Application in combination with a steam turbine
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2220/00—Application
    • F05D2220/70—Application in combination with
    • F05D2220/76—Application in combination with an electrical generator
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E20/00—Combustion technologies with mitigation potential
    • Y02E20/14—Combined heat and power generation [CHP]
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E20/00—Combustion technologies with mitigation potential
    • Y02E20/16—Combined cycle power plant [CCPP], or combined cycle gas turbine [CCGT]

Definitions

  • the invention relates to a gas and steam turbine plant with a generator, a gas turbine and a steam turbine. It further relates to a method for operating such a system.
  • the effluent from a gas turbine hot exhaust gases are used to heat a so-called heat recovery steam generator, which generates by evaporating ⁇ tion of liquid water necessary for the operation of a steam turbine steam.
  • the gas turbine and the steam turbine serve to drive one or more electrical generators for generating electrical energy.
  • the provision of steam as heating steam for district heating applications or as process steam in the chemical or other industries can be a design target for a cogeneration plant operating in combined heat and power (combined heat and power).
  • the combined cycle process is gen part of the steam entzo ⁇ so that the stored in it energy content not to operate the steam turbine to generate electricity or is available.
  • heat and power CHP plants a distinction is made between heat and power CHP plants depending on the priority assigned to each of the two forms of energy: electricity-led plants optimize the electricity yield, heat led plants the heat yield, in each case at the expense of the other form of energy.
  • a steam turbine can be operated either in counter-pressure operation or in condensation mode.
  • Kondensationsbe ⁇ operating range of the expansion of the steam turbine is a condensate ⁇ sator downstream prevails in the result of the cooling and condensation of the incoming low-pressure steam by means of cooling water ⁇ a vacuum. After the expansion work has been carried out, the steam is to a certain extent removed from the
  • a gas turbine and a first generator are arranged on a first shaft.
  • a second shaft independent of the first shaft in this so-called "cross-compound" design usually a high-pressure stage and optionally a medium-pressure stage, which drive a second generator connected to the second shaft, are arranged as components of a steam turbine system.
  • a third shaft independent of the first and the second shaft is provided, to which a low-pressure part turbine and a third ter generator are coupled.
  • the invention is therefore based on the object of specifying a gas and steam turbine plant of the type mentioned above, which permits different modes with varying Dampfaus ⁇ coupling with simple construction and highPoltrials ⁇ degree. It is also intended to specify a method suitable for operating such a gas and steam turbine plant.
  • the object is achieved by the generator, the gas turbine and the steam turbine are arranged on a shaft having a number of wave segments, the steam turbine each having a shaft segment associated high-pressure stage and a Nie ⁇ derdrucklane includes, wherein the Low-pressure stage ⁇ assigned shaft segment is arranged end to the shaft, and wherein between the shaft segment of the high-pressure stage and the shaft segment of the low-pressure stage at least one clutch ment is provided.
  • the invention is based on the consideration that a single-shaft arrangement for a cogeneration plant operated gas and steam turbine plant is advantageous because in this way the above-described disadvantages of Mehrwel ⁇ lenan Aunt are avoided.
  • only a single generator is needed.
  • the steam turbine of the combined cycle plant should be constructed in several stages in order to provide structurally simple and operationally safe way sampling points for heating or process steam with defined steam parameters between the pressure stages of the steam turbine. It should have at least one high-pressure stage and a low pressure stage ⁇ be provided for each illustrate a conventional and proven design can be used. In this way, a comparatively complicated design of a steam turbine ⁇ turbine as a removal turbine is not required.
  • a regular bare removal device for heating or process steam is arranged within a rather high pressure stage and the low-pressure stage steam side connects Denden overflow at the now provided system.
  • the steam between these two pressure stages can also be supplied to a medium-pressure stage and / or reheating.
  • the shaft segments associated with the high-pressure stage and the low-pressure stage are rigidly connected to one another, the low-pressure stage must always run at the same speed as the high-pressure stage. For reasons of operational safety, even in the case of a Taking mode of the steam turbine arrangement, a partial flow of the steam mass flow for cooling the low pressure stage are passed through the ⁇ se. The steam required for cooling is thus lost for the desired heating power or other uses with process steam demand.
  • the low-pressure stage can also be coupled by means of the coupling as needed to the shaft driving the generator.
  • a derar ⁇ term condensation operation ie coupled with low-pressure stage and a steam side downstream condenser, then a particularly high electrical power can be generated and provided to a customer or power consumers available.
  • the generator can be arranged at the end of the shaft of the gas and steam turbine plant, so that the gas turbine is located axially between the generator and the steam turbine. In a preferred variant, however, the generator is arranged axially between the gas turbine and the steam turbine.
  • the combined cycle power plant in addition to the high-pressure stage and low pressure stage also a With ⁇ teldrucklane, which vorteilhafter- flow medium side way between the high pressure stage and the low pressure stage is connected.
  • ⁇ da is connected with the medium pressure stage on a common shaft segment with the high pressure stage.
  • the rotor of the high-pressure stage and the rotor of the medium-pressure stage always rotate at the same speed.
  • spatially separate housing can be provided. However, they can also advantageously be accommodated in a common housing and in this way form a combined high / medium pressure turbine.
  • the middle ⁇ pressure stage can also be connected via a common shaft segment with the low-pressure stage and form a unit with this respect Lich ⁇ the rotational movement.
  • the unit formed by the intermediate-pressure stage and the low-pressure stage is decoupled as required from the high-pressure stage shaft segment connected to the generator as required.
  • the medium-pressure turbine and the low-pressure turbine may be formed by arranged in separate casings sub-turbines or housed in a common housing. If separate housing for the medium-pressure stage and the low-pressure stage are provided, which Niederdruckstu ⁇ fe is advantageously in the form of a double-flow low-pressure turbine section is formed.
  • the or each clutch is a shift ⁇ clutch.
  • the abovementioned object is achieved by disconnecting one or more pressure stages of the steam turbine from the generator or by coupling them to the generator, depending on the demand for heating and process steam and / or the demand for electrical energy.
  • the designed for a Kondensati ⁇ ons congress low pressure stage is connected as required by virtue of a coupling with the drive shaft or separated from it.
  • the clutch is configured as a clutch.
  • the method can, however, in principle also in a gas and steam turbine plant with a non-switchable coupling between the pressure levels, such as a pin clutch or the like, apply, especially if the modes with open or closed clutch are changed only relatively rarely. This could be the case, for example, in a cogeneration plant, which should provide heating steam only during the winter months.
  • the steam turbine can be operated both in the condensation mode and in the counter-pressure mode by means of the coupling arranged between two vapor pressure stages of a combined cycle gas turbine system, the disadvantages of conventional multi-shaft arrangements being avoided.
  • condensing mode with the clutch engaged the entire mass flow of steam passes through the low-pressure turbine section therethrough, and there is a maximum electric power ⁇ he witnesses. If a part of the turbine, so either the low-pressure part ⁇ turbine alone or the low pressure stage together with a medium-pressure stage, disconnected and shut down, no cooling steam supply is necessary for the disconnected part. After the last pressure stage in operation, the complete steam can be removed from the gas and steam process and used as heating or process steam.
  • a rapid switchover between a maximum power generation and a maximum steam extraction mode of operation of the gas and steam turbine plant is possible.
  • Figures 1 to 6 are each a schematic block diagram of a first to sixth variant of a gas and steam turbine plant according to the present invention ⁇ .
  • the gas and steam turbine plant 2 shown in FIG 1 Be ⁇ component of a combined cycle power plant.
  • the gas and steam turbine plant 2 has an electric generator 4, a gas turbine 6 and a steam turbine 8.
  • the steam turbine 8 comprises a high-pressure stage 8a, a medium-pressure stage 8b and a low-pressure stage 8c.
  • the respective pressure conditions present during operation are also identified by the lettering HD, MD or ND in FIG.
  • the resulting during the combustion of a fossil fuel in the gas turbine 6 hot exhaust gases are used for heating a Abhitzedampferzeu ⁇ not shown here gers in which steam is generated by steam for operation of the steam turbine 8.
  • the gas turbine 6, the steam turbine ⁇ 8 and the generator 4 are connected in a so-called Einwellenan- order on a aligned along a common axis shaft 10 in series, in the present case, the generator 4 in the axial direction between the gas turbine 6 and the steam turbine. 8 is arranged.
  • the torque applied by the gas turbine 6 and the steam turbine 8 to the shaft 10 serves to drive the generator 4.
  • the electric current generated in the generator 4 is fed into a power grid, not shown in greater detail.
  • the high pressure stage 8a of the steam turbine 8 is supplied in the operating case via a main steam line 12 with live steam, which is provided by the not shown here, the gas turbine 6 flue gas downstream heat recovery steam generator.
  • the steam passes after entering the high pressure stage 8 a high-pressure expansion distance, WO expands to perform work on it and means of timing ⁇ support on the turbine blades the rotor as part of the high pressure stage drives 8a associated shaft segment.
  • the partially ent ⁇ after exiting from the high pressure stage 8a spanned steam is supplied via an overflow line 14 a here only schematically indicated reheater 16, wherein increased at approximately constant pressure its temperature. It is then added to the medium-pressure stage 8b.
  • the HD section 8a faces the generator 4 and the MD section 8b of the low-pressure stage 8c. After flowing from the medium-pressure stage 8b, the already relaxed to a low pressure and temperature level steam via a further overflow 18 of the low pressure stage 8c can be fed.
  • the overflow line 18 in this case has a branch 20 for the removal of heating or process steam, wherein the ratio ⁇ nis of the two partial mass flows generated in this way by two arranged in each line branch valves
  • the removable at the junction 20 as needed heating or process steam is supplied via a Dampflei ⁇ device 26 of a technical system not shown here or an industrial operation. If no heating or process steam is required, the valve 24 is thus closed, the entire mass flow leaving the middle pressure stage 8b is supplied to the low-pressure stage 8c when the valve 22 is open.
  • the low pressure stage 8c is the output side of a capacitor not shown here downstream, in which the exiting vapor at a pressure of almost zero bar almost completely relaxed and thereby condenses to liq ⁇ sigem water, which then fed again into the water-steam cycle of the steam turbine plant becomes.
  • an additional torque is impressed on the shaft 10 in the low-pressure stage 8c, so that the entire CCGT process is optimized for generating a high electrical power.
  • the gas and steam turbine plant 2 also provides in the other case, namely that the highest possible steam mass flow after the outflow from the medium pressure stage 8b is to be coupled out for use as heating or process steam, a particularly high efficiency.
  • the shaft segment associated with the low-pressure stage 8c can be decoupled and shut down by means of a clutch 28 from the shaft segment assigned to the combined HD / MD turbine 8a, 8b and thus also from the generator 4. Since no partial mass flow of the steam more than cooling steam must be passed through the low pressure stage 8c at disused low pressure stage 8c, the valve 22 can and should be completely closed in this case. This leaves the entire effluent from the medium-pressure stage 8b steam mass flow for heating purposes ⁇ or other applications. In addition, friction losses, as would occur in a rigidly connected to the rest of the shaft train and inevitably "idle" with ⁇ rotating low pressure stage 8c, completely eliminated.
  • the high-pressure stage 8a and the medium-pressure stage 8b are accommodated in separate housings, wherein an additional clutch 30 is provided between these two pressure stages.
  • the intermediate-pressure stage 8b can therefore additionally be decoupled from the rest of the drive train acting on the generator 4 and shut down, depending on whether a withdrawal of process steam at a medium or low pressure level is desired.
  • the steam-side connection of the pressure stages 8a, 8b, 8c which is not shown in detail here, this corresponds Wesent ⁇ union known from FIG 1 configuration, but has, between the high pressure stage 8a and the medium-pressure stage 8b further extraction or Abzapfstellen for process steam and corresponding valves for controlling the partial mass flows.
  • the medium-pressure stage 8b and the low-pressure stage 8c are arranged on a common shaft segment and can therefore only be decoupled from the high-pressure stage 8a and shut down together.
  • This variant is especially advantageous if no external need for Low pressure steam exists. Then the coupling 26 known from FIG. 1 can be omitted between the medium-pressure stage 8b and the low-pressure stage 8c.
  • FIGS. 4 to 6 correspond to the configurations already known from FIGS. 1 to 3, with the difference that a further clutch 32 is provided in each case between the high-pressure stage 8a and the generator 4.
  • a further clutch 32 is provided in each case between the high-pressure stage 8a and the generator 4.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)

Abstract

L'invention concerne une installation à turbine à gaz et à vapeur (2) qui comprend un générateur (4), une turbine à gaz (6) et une turbine à vapeur (8). L'invention vise à fournir une telle installation qui convienne à différents modes de fonctionnement avec extraction variable de la vapeur, tout en conservant une conception simple et en assurant un rendement global élevé. A cet effet, le générateur (4), la turbine à gaz (6) et la turbine à vapeur (8) sont placés sur un arbre (10) présentant un certain nombre de segments d'arbre. La turbine à vapeur (8) comprend un étage haute pression (8a) affecté respectivement à un segment d'arbre et un étage basse pression (8c), le segment d'arbre affecté à l'étage basse pression (8c) étant situé à l'extrémité de l'arbre (10). Au moins un accouplement (28, 30) est prévu entre le segment d'arbre de l'étage haute pression (8a) et le segment d'arbre de l'étage basse pression (8c).
PCT/EP2006/063874 2005-07-15 2006-07-04 Installation a turbine a gaz et a vapeur, ainsi que procede pour la faire fonctionner WO2007009874A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP06777567.6A EP1904731B1 (fr) 2005-07-15 2006-07-04 Installation combinée de turbines à gaz et à vapeur et son procédé de fonctionnement

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
EP05015455A EP1744032A1 (fr) 2005-07-15 2005-07-15 Installation combinée de turbines à gaz et à vapeur et son procédé de fonctionnement
EP05015455.8 2005-07-15

Publications (1)

Publication Number Publication Date
WO2007009874A1 true WO2007009874A1 (fr) 2007-01-25

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ID=34937865

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2006/063874 WO2007009874A1 (fr) 2005-07-15 2006-07-04 Installation a turbine a gaz et a vapeur, ainsi que procede pour la faire fonctionner

Country Status (4)

Country Link
EP (2) EP1744032A1 (fr)
CN (1) CN100564832C (fr)
PL (1) PL1904731T3 (fr)
WO (1) WO2007009874A1 (fr)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2305964A1 (fr) 2009-09-23 2011-04-06 Siemens Aktiengesellschaft Centrale à vapeur
EP2395205A1 (fr) 2010-06-10 2011-12-14 Alstom Technology Ltd Centrale électrique dotée de capture et de compression de CO2
EP2700790A1 (fr) * 2012-08-21 2014-02-26 Siemens Aktiengesellschaft Centrale électrique comprenant une turbine à gaz, un générateur et une turbine à vapeur et procédé de son opération
GB2524582B (en) * 2014-03-28 2016-07-20 Mitsubishi Hitachi Power Sys Combined cycle gas turbine plant
EP3511535A1 (fr) 2018-01-10 2019-07-17 Siemens Aktiengesellschaft Installation et procédé de fonctionnement d'une installation
DE102022202265A1 (de) * 2022-03-07 2023-09-07 Siemens Energy Global GmbH & Co. KG Dampfturbinenanlage

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0407132A1 (fr) * 1989-07-03 1991-01-09 General Electric Company Cycle combiné couplé par arbre commun
DE4426354A1 (de) * 1994-07-25 1996-02-01 Abb Management Ag Kombianlage
EP1264966A1 (fr) * 2000-02-10 2002-12-11 Kabushiki Kaisha Toshiba Turbine a vapeur et equipement de generation de puissance
JP2004137912A (ja) * 2002-10-15 2004-05-13 Mitsubishi Heavy Ind Ltd ガスタービン複合発電プラント

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0407132A1 (fr) * 1989-07-03 1991-01-09 General Electric Company Cycle combiné couplé par arbre commun
DE4426354A1 (de) * 1994-07-25 1996-02-01 Abb Management Ag Kombianlage
EP1264966A1 (fr) * 2000-02-10 2002-12-11 Kabushiki Kaisha Toshiba Turbine a vapeur et equipement de generation de puissance
JP2004137912A (ja) * 2002-10-15 2004-05-13 Mitsubishi Heavy Ind Ltd ガスタービン複合発電プラント

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN vol. 2003, no. 12 5 December 2003 (2003-12-05) *

Also Published As

Publication number Publication date
EP1904731A1 (fr) 2008-04-02
CN100564832C (zh) 2009-12-02
EP1904731B1 (fr) 2017-03-01
CN101218426A (zh) 2008-07-09
EP1744032A1 (fr) 2007-01-17
PL1904731T3 (pl) 2017-08-31

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